CN103732964A - Expansion valve device - Google Patents
Expansion valve device Download PDFInfo
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- CN103732964A CN103732964A CN201280040408.0A CN201280040408A CN103732964A CN 103732964 A CN103732964 A CN 103732964A CN 201280040408 A CN201280040408 A CN 201280040408A CN 103732964 A CN103732964 A CN 103732964A
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- refrigeration agent
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- 239000003507 refrigerant Substances 0.000 claims abstract description 98
- 238000005057 refrigeration Methods 0.000 claims description 115
- 239000003795 chemical substances by application Substances 0.000 claims description 71
- 230000008859 change Effects 0.000 claims description 32
- 230000006837 decompression Effects 0.000 claims description 14
- 230000001007 puffing effect Effects 0.000 claims description 12
- 238000006073 displacement reaction Methods 0.000 claims description 9
- 238000010438 heat treatment Methods 0.000 description 58
- 230000004308 accommodation Effects 0.000 description 25
- 230000004087 circulation Effects 0.000 description 23
- 239000006200 vaporizer Substances 0.000 description 22
- 238000004378 air conditioning Methods 0.000 description 18
- 238000007791 dehumidification Methods 0.000 description 17
- 238000007599 discharging Methods 0.000 description 13
- 125000004122 cyclic group Chemical group 0.000 description 9
- 238000010586 diagram Methods 0.000 description 9
- 230000001276 controlling effect Effects 0.000 description 8
- 238000001816 cooling Methods 0.000 description 8
- 238000011144 upstream manufacturing Methods 0.000 description 8
- JEIPFZHSYJVQDO-UHFFFAOYSA-N ferric oxide Chemical compound O=[Fe]O[Fe]=O JEIPFZHSYJVQDO-UHFFFAOYSA-N 0.000 description 7
- 230000005855 radiation Effects 0.000 description 7
- 238000000034 method Methods 0.000 description 6
- 238000006243 chemical reaction Methods 0.000 description 5
- GOLXNESZZPUPJE-UHFFFAOYSA-N spiromesifen Chemical compound CC1=CC(C)=CC(C)=C1C(C(O1)=O)=C(OC(=O)CC(C)(C)C)C11CCCC1 GOLXNESZZPUPJE-UHFFFAOYSA-N 0.000 description 5
- 230000004913 activation Effects 0.000 description 4
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 3
- 238000001514 detection method Methods 0.000 description 3
- 239000007769 metal material Substances 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- CNQCVBJFEGMYDW-UHFFFAOYSA-N lawrencium atom Chemical compound [Lr] CNQCVBJFEGMYDW-UHFFFAOYSA-N 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000010257 thawing Methods 0.000 description 2
- 239000006096 absorbing agent Substances 0.000 description 1
- 229910002092 carbon dioxide Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 230000001815 facial effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000696 magnetic material Substances 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000003595 mist Substances 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
- F16K31/047—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
- B60H1/3205—Control means therefor
- B60H1/3213—Control means therefor for increasing the efficiency in a vehicle heat pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
- F25B41/35—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by rotary motors, e.g. by stepping motors
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Abstract
A drive control device (10) performs, at a constant current, mode switching between a first mode in which the degree of opening of a refrigerant path (51a) is changed in a first flow rate range in which the flow rate of a refrigerant flowing through the refrigerant path (51a) is less than or equal to a predetermined flow rate, and a second mode in which the degree of opening of the refrigerant path is changed in a second flow rate range in which the flow rate of the refrigerant flowing through the refrigerant path exceeds the predetermined flow rate. A constant current value (A2) at which mode switching is performed is increased by the drive control device to a value greater than a constant current value (A1) at which the degree of opening of the refrigerant path is changed at the constant current in the first mode.
Description
The cross reference of related application
The Japanese patent application No.2011-208295 that the disclosure was filed an application based on September 24th, 2011, the content of this application is incorporated in full at this by reference.
Technical field
The disclosure relates to a kind of expansion valve device.
Background technique
Patent documentation 1 has been described a kind of for controlling the mortor operated valve (electric expansion valve) of the flow of refrigeration agent.Mortor operated valve has the valve member that utilizes stepping motor to open or close the valve port of fluid passage.Mortor operated valve has reduction gear, and the rotation of the rotor of stepping motor output is transferred to by reduction gear the screw mechanism that valve member is moved.Therefore, obtain powerful valve control force and high-resolution valve opening degree feature.
Can by electric expansion valve, guarantee high output and high flow capacity control accuracy from Small Flow Control region to large flow control region.Yet, for example, when valve opening degree is during from Small Flow Control area change to large flow control region, or when valve opening degree is during from large flow control area change to Small Flow Control region, need to expend time in valve member is moved.That is,, while being switched when the pattern pattern that valve opening degree changes in Small Flow Control region therein and between the pattern that wherein valve opening degree changes in large flow control region, need to expend the valve opening degree that the long period reaches setting.
Prior art document
Patent documentation 1:JP-2006-226369A
Summary of the invention
Object of the present disclosure is to provide a kind of situation that can shorten execution pattern change between the pattern that valve opening degree changes in Small Flow Control region therein and the pattern that wherein valve opening degree changes in large flow control region and is issued to the target valve opening degree expansion valve device of spent time cycle.
According to an example of the present disclosure, be arranged in refrigeration cycle so that cycle through the refrigeration agent decompression of refrigeration cycle and the expansion valve device expanding comprises housing, valve member, Vidacare corp and driving-controlling device.Housing limits the refrigerant passage that refrigerant circulation passes through.Valve member is arranged in housing to change the opening degree of refrigerant passage.Vidacare corp has stepping motor with by making valve member displacement control the opening degree of refrigerant passage according to the angle of swing of stepping motor.Driving-controlling device is with constant current driven and control step motor.Driving-controlling device changes with steady current execution pattern between first mode and the second pattern, in described first mode, the opening degree of refrigerant passage changes in the first flow region less than or equal to predetermined value at the flow of refrigeration agent that flows through refrigerant passage, in described the second pattern, the opening degree of refrigerant passage changes in the second flow region higher than described predetermined value at the flow of refrigeration agent that flows through refrigerant passage, and the value of steady current when driving-controlling device increase pattern changes is to be greater than the value of steady current used when the opening degree of refrigerant passage changes in first mode.
Therefore,, even when the voltage from power supply supply changes, driving-controlling device also can stably drive stepping motor by steady current.In addition, when the opening degree of refrigerant passage is therein flowing through between the second pattern changing in the first mode that changes in first flow region of the flow of the refrigeration agent of refrigerant passage less than or equal to predetermined value and the flow of refrigeration agent that wherein opening degree of refrigerant passage is flowing through refrigerant passage the second flow region higher than described predetermined value that execution pattern changes, the current value of constant current driven is increased to be greater than the current value using when the opening degree of refrigerant passage changes under first mode.Therefore, the moment of torsion being produced by stepping motor increases so that therefore valve member displacement can promptly change valve opening degree.
Therefore, when execution pattern changes when the opening degree of refrigerant passage changes in Small Flow Control region therein pattern and between the pattern that wherein opening degree of refrigerant passage changes in large flow control region, can shorten the spent time of valve opening degree that reaches setting.
Further, for example, driving-controlling device has the reducing gear that the rotation of stepping motor is slowed down, and valve member by reducing gear the swing offset by stepping motor.Be equipped with and make the expansion valve device of the reducing gear that the rotation of stepping motor slows down can realize the high control accuracy that flows, but when changing valve opening degree, expending the plenty of time moves valve member.Therefore, the disclosure is applied to be equipped with the expansion valve device of reducing gear very effective.
Further, for example, when the temperature of driving-controlling device is during higher than predetermined value, or when the value of the physical quantity relevant with temperature is during higher than predetermined threshold, even when pattern changes, driving-controlling device also forbids that current value increases.
If temperature uprises, the function of driving-controlling device may reduce.Therefore, when the temperature of the assembly of driving-controlling device surpasses predetermined value, or when the value of the physical quantity relevant with temperature is during higher than predetermined threshold, even if also forbid that when pattern changes current value increases, thereby limit the temperature increase of driving-controlling device.Therefore, can limit driving-controlling device and there is functional error.
Further, for example, first mode is the puffing pattern that wherein refrigeration agent is depressurized and expands in the first flow region in the time need to making to flow through the refrigeration agent decompression of refrigerant passage, and the second pattern be wherein when not needing to make to flow through the refrigeration agent decompression of refrigerant passage valve member make the opening degree of refrigerant passage maximum so that flow through the full opening mode that the flow of the refrigeration agent of refrigerant passage becomes maximum at the second flow region.
Therefore, therein refrigeration agent at the flow of refrigeration agent that flows through refrigerant passage, in the small flow region less than or equal to predetermined value, be depressurized and expand puffing pattern time, by making valve member displacement control refrigerant flow with precision relatively fully.Further, when in puffing pattern and when wherein the opening degree of refrigerant passage is formed between maximum full opening mode execution pattern and changes by valve member, promptly execution pattern changes.
Further, for example, first mode is the first puffing pattern that wherein refrigeration agent is depressurized and expands in the first flow region, and the second pattern is the second puffing pattern that wherein refrigeration agent is depressurized and expands in the second flow region, and the value of the steady current of driving-controlling device increase pattern while changing is to be greater than the value of the steady current being used when the value of the steady current being used when opening degree changes in first mode and opening degree change in the second pattern.
Therefore, therein refrigeration agent at the flow of refrigeration agent that flows through refrigerant passage, in the small flow region less than or equal to predetermined value, be depressurized and expand puffing pattern time and refrigeration agent is flowing through the refrigeration agent of refrigerant passage therein flow be depressurized in surpassing the large flow region of predetermined value and expand puffing pattern time, by making valve member displacement control refrigerant flow with precision relatively fully.Further, when between the puffing pattern in the puffing pattern in small flow region and large flow region, execution pattern changes, promptly execution pattern changes.
Accompanying drawing explanation
Fig. 1 is that diagram is according to the schematic diagram of an embodiment's expansion valve device;
Fig. 2 is the schematic diagram that diagram has the automotive air conditioner of expansion valve device;
Fig. 3 is the plotted curve that is shown in the relation between valve opening degree and refrigerant flow under each operator scheme of refrigeration cycle;
Fig. 4 is the flow chart that valve opening degree that the driving-controlling device of diagram by expansion valve device carries out is controlled; And
Fig. 5 is the rotating speed of motor and the plotted curve of the relation between generation moment of torsion of diagram expansion valve device.
Embodiment
Fig. 1 is that diagram is corresponding to the sectional view (partly comprising skeleton diagram) with the air conditioning control gear 10 of variable throttle valve 50 and this variable throttle valve 50 of control according to the heating of an embodiment's expansion valve device.Fig. 2 shows the vehicle air conditioner equipment that uses variable throttle valve 50.
As shown in Figure 2, air regulator equipment has the air-conditioning unit 1 of the passenger accommodation of vehicle being carried out to air conditioning.Air conditioning part (actuator) in air-conditioning unit 1 is controlled by air conditioning control gear 10 (ECU).Air-conditioning unit 1 comprise there is conduit 2, the refrigeration cycle 3 of centrifugal blower, vaporizer 27 and gas cooler 22.Conduit 2 limits the air of adjusting is incorporated into the air flue in passenger accommodation.Blower produces the air-flow towards passenger accommodation in conduit 2.Vaporizer 27 cooled flow are by the air of conduit 2.Gas cooler 22 heats by the air of vaporizer 27 again.
A plurality of air outlet slit (not shown) are limited to the downstream of conduit 2 along air-flow direction.Outlet comprises at least defroster vent (DEF), face outlet (FACE) and foot's outlet (FOOT).Defroster vent mainly blows to hot air the internal surface of the windshield of vehicle.Face outlet mainly blows to cool air passenger's the upper part of the body (head and chest).Foot's outlet mainly blows to hot air passenger's the lower part of the body (foot).Air outlet slit changes door (not shown) by a plurality of patterns and is selectively opened or closes.Pattern changes door and is driven by the actuator 14 such as servomotor, so Bas Discharged pattern (MODE) is switched between facial model (FACE), two-stage pattern (B/L), foot's pattern (FOOT), foot's defrosting mode (F/D) and defrosting mode (DEF).
Centrifugal blower has centrifugal fan 5 and makes the blower motor 16 of fan 5 rotations.Fan 5 is rotatably contained in along air-flow direction and is integrally formed in the spiral case of upstream side of conduit 2.The terminal voltage of the blower motor 16 of the rotating speed of motor 16 based on applying by blower drive circuit (not shown) (air compressor control voltage, blower level) changes, and makes it possible to control the amount that sends to the air in passenger accommodation.
The first decompressor consists of variable throttle valve 50, and wherein gas refrigerant flow into described variable throttle valve 50 from gas cooler 22.Variable throttle valve 50 is first decompressors that the refrigeration agent flowing out from gas cooler 22 reduced pressure based on valve opening degree, and can be corresponding to the moving expansion valve (EVH) of heating electric.Valve opening degree carries out electrical control by ECU10.In addition, variable throttle valve 50 can be arranged to have full opening mode by ECU10, makes to open completely the valve opening degree of variable throttle valve 50.
Inner heat exchanger is that superheating will be inhaled into the refrigeration agent-refrigerant heat exchanger in the entry port of compressor 21.Between the low-temperature refrigerant of the high temperature refrigerant flowing out in outlet from outdoor heat converter 24 and outlet outflow from reservoir 28, carry out heat exchange.Inner heat exchanger has two-layer heat exchange structure, and wherein the surperficial close contact of the surface of low-temperature side heat exchanger 29 and h 25 is can carry out heat exchange.
The second compressor has for cooling variable throttle valve 26 and bypass tube 33.Refrigeration agent flow into throttle valve 26 from the h 25 of inner heat exchanger.The refrigeration agent flowing out from the h 25 of inner heat exchanger is because pipe 33 is walked around throttle valve 26 and vaporizer 27 is sent to reservoir 28.Variable throttle valve 26 is second decompressors that the refrigeration agent of h 25 outflows from inner heat exchanger reduced pressure based on valve opening degree.Variable throttle valve 26 is for cooling electric expansion valve (EVC), and by ECU10, valve opening degree is carried out to electronic control.Electromagnetism close/open valve 34 (VH: be called as below heating electric magnet valve) is arranged in pipe 33.When supply electric power (ON), valve 34 is opened, and valve 34 cuts out when stopping power supply (OFF).
Vaporizer 27 is air-refrigerant heat exchanger (heat absorbers).The refrigeration agent being depressurized by throttle valve 26 carries out heat exchange by the air with being sent by fan 5 and is evaporated.The heat of air is absorbed by vaporizer 27.Vaporizer 27 is supplied to gas refrigerant by reservoir 28 low-temperature side heat exchanger 29 and the compressor 21 of inner heat exchanger.Reservoir 28 is to have the gas-liquid separating appts that stores the apotheca of the refrigeration agent flowing out from vaporizer 27 for interim.
The circulation loop switching part of refrigeration cycle 3 switches between the operator scheme of refrigeration cycle 3, that is, the circulation route of the refrigeration agent in refrigeration cycle 3 is switched between at the circulation loop for refrigerating mode (cool cycles), for the circulation loop (Heating Cyclic) of heating mode and the circulation loop (dehumidifying circulation) for dehumidification mode or dehumidifying heating mode.In the present embodiment, variable throttle valve 50 and solenoid valve 34 can be corresponding to circulation loop switching parts.
Particularly, when heating has full opening mode by variable throttle valve 50, and when heating electric magnet valve 34 is closed, the operator scheme of refrigeration cycle 3 is set to cool cycles (for the circulation loop of refrigerating mode).In addition, when valve 50 has that wherein refrigeration agent is depressurized and expands to have the pressure reducing mode of small flow, and when valve 34 is opened, the operator scheme of refrigeration cycle 3 is set to Heating Cyclic (for the circulation loop of heating mode).In addition, when valve 50 has pressure reducing mode, and when valve 34 is closed, the operator scheme of refrigeration cycle 3 is set to dehumidifying circulation (for the circulation loop of dehumidification mode).
Here, the refrigeration cycle 3 of the present embodiment is used its main component by the carbon dioxide (CO with low critical temperature
2) refrigeration agent that forms.Refrigeration cycle 3 is the circulations of supercritical steam compression heat pump.The refrigeration agent of discharging from the discharge port of compressor 21 has the high pressure of the critical pressure of being equal to or higher than.In the circulation of supercritical steam compression heat pump, the refrigerant temperature of the entrance part of gas cooler 22 (inlet temperature of refrigeration agent) is increased to about 120 ℃ by increasing on high-tension side refrigerant pressure.That is the temperature of the refrigeration agent of, discharging from the discharge port of compressor 21 is increased to about 120 ℃.In addition, though refrigeration agent by heat radiation in gas cooler 22, flowing into refrigeration agent in gas cooler 22 can condensation yet, this is because refrigeration agent is pressurizeed to have the pressure of the critical pressure of being equal to or higher than by compressor 21.
ECU10 comprises known microcomputer, described microcomputer for example have carry out control procedure and computational process CPU, store storage (ROM, RAM), I/O port and the timer function of various programs and data.When the ignition switch of vehicle is connected (IG-ON), electric power is supplied to ECU10.The control signal of ECU10 based on from air regulator control panel (not shown) input, for example, from the sensor signal of various sensors inputs be stored in each actuator (, servomotor 13-15, blower 16, variable throttle valve 26,50, solenoid valve 34 and transducer 20) that control program storage is electrically controlled air-conditioning unit 1.
Air regulator control panel has temperature setting switch, air regulator (A/C) switch, air inlet configuration switch (FRS/REC switch), air outlet slit configuration switch (mode switch), windshield heater (DEF) switch, air quantity switch, automatic (AUTO) switch, closes (OFF) switch etc.Air regulator (A/C) switch is that instruction is carried out the cooling of cooling or dehumidifying or dehumidifying switch to passenger accommodation.Air regulator (A/C) switch be instruction refrigerating mode or dehumidification mode in the operator scheme of refrigeration cycle 3 cooling/configuration part of dehumidifying.The compressor 21 of refrigeration cycle 3 can be forced to drive by opening A/C switch, and can be forced to stop by closing A/C switch.
DEF switch is that instruction is fixed into Bas Discharged pattern the DEF pattern floatless switch of DEF pattern.DEF switch is to remove the mist of windshield or prevent the anti-switch that hazes that windshield hazes.Further, DEF switch is that instruction is fixed to the operator scheme of refrigeration cycle 3 the dehumidification mode selection portion of dehumidification mode.Dehumidification mode selection portion is set as dehumidifying mode of priority or is blowed the dehumidification mode of in temperature prioritised pattern.Alternatively, gone out outside DEF switch, dehumidification mode selection portion can be to detect the anti-sensor that hazes hazing of windshield.Dehumidification mode selection portion can be the dehumidifying switch that only instruction dehumidifies in passenger accommodation in the situation that Bas Discharged pattern not being fixed to DEF pattern when switch is switched on.Dehumidification mode selection portion can be in the situation that Bas Discharged pattern not being fixed to DEF pattern, only ordering and prevent the anti-switch that hazes that windshield hazes when switch is switched on.
Recloser is that at least based target blows temperature (TAO) and the operator scheme of refrigeration cycle 3 is set to the switch of refrigerating mode, heating mode or dehumidification mode.Recloser is to carry out order automatically to control the automatic control switch of each actuator of air-conditioning unit 1.For example,, when pattern changes switch or air quantity configuration switch and is operated, for switching Bas Discharged pattern or regulating to control and be cancelled for controlling the automatic air of blower motor.
External air temperature sensor 44 detects the temperature (TAM) as the outside air of the air temperature of passenger accommodation outside.Temperature transducer 45 (this temperature transducer can corresponding to dehumidifying effect detector of the present disclosure) detects the immediately air temperature in the downstream of vaporizer 27 (TE: hereinafter referred to as temperature after vaporizer).Inside Air Temperature sensor 46 detects the temperature (TR) as the inner air of the air temperature of passenger accommodation inside.Solar energy sensor 47 detects the solar radiation quantity (TS) that enters into passenger accommodation.Temperature transducer 48 (this temperature transducer can corresponding to heating efficiency detector of the present disclosure) detects immediately the air temperature in the downstream of gas cooler 22 (TGC: be designated hereinafter simply as temperature after gas cooler).From the sensor signal of sensor 44,45,46,47 and 48 outputs, at A/D change-over circuit, there is A/D conversion, and the signal after conversion is imported in microcomputer.
Below the operation of the Short Description apparatus of air conditioning hereinafter.
For example, when ignition switch is in on-state and when electric power is supplied to ECU10, the control signal of each the switch (not shown) transmission of ECU10 based on from air regulator control panel, from the sensor signal of various sensor transmissions be stored in the operator scheme that control program storage is selected refrigeration cycle 3.Therefore, each actuator of air-conditioning unit 1 (servomotor 13-15, blower 16, variable throttle valve 26,50, solenoid valve 34 and transducer 20) is by electric control.
For example, when recloser is opened to carry out automatic air and regulate controls, ECU10 receives from the sensor signal of various sensors with from the control signal of air regulator control panel.Described signal is that each air conditioning member (actuator) of controlling in air-conditioning unit 1 is necessary.Next, the target that is blown into the adjusting air in passenger accommodation based on pre-stored formula calculating in storage blows temperature (TAO).
Next, for example based on air regulator (A/C) switch, carry out the compressor operation judgement for determining whether compressor 21 is switched on or stops.When the result indication of compressor operation judgement blows 21 connection of temperature (TAO) compressor according to the target of previously calculating, implement either operational mode judges to determine the operator scheme of refrigeration cycle 3.
In operator scheme is judged, comparison object blows temperature (TAO) and the first specified value (for example, 45 ℃) and the second specified value (for example, 15 ℃).The in the situation that of TAO >=α, select Heating Cyclic (heating mode) as the operator scheme of refrigeration cycle 3.The in the situation that of TAO≤β, select cool cycles (refrigerating mode) as the operator scheme of refrigeration cycle 3.The in the situation that of β <TAO< α, select dehumidifying circulation (dehumidification mode) as the operator scheme of refrigeration cycle 3.
After selecting the operator scheme of refrigeration cycle 3, determine be applied to blower motor 16 terminal voltage (air compressor control voltage, blower level), change the opening degree that air enters the door 4 of pattern (between inner air pattern and exterior air patterns), the pattern that changes Bas Discharged pattern is switched the opening degree of door and the opening degree (A/M opening degree) of A/ M door 6,7, and is controlled actuator with blower and door.
Set the operator scheme of refrigeration cycle 3.Serviceability (rotating speed etc.), the opening degree of variable throttle valve 50,26 and the opening/closing state of solenoid valve 34 of setting and control compressor 21 are maximized the cycle efficiency of refrigeration cycle 3 in each operator scheme.
When selecting refrigerating mode as the operator scheme of refrigeration cycle 3, variable throttle valve 50 has full opening mode, and solenoid valve 34 is closed.The refrigeration agent of discharging from the outlet of compressor 21 circulates in the following sequence: gas cooler 22, clear way valve 50, outdoor heat converter 24, h 25, valve 26, vaporizer 27, reservoir 28, low-temperature side heat exchanger 29 and compressor 21 are (as shown in the blank direction of arrow by Fig. 2, in the circulation loop for refrigerating mode, cool cycles).
Now, the opening degree of controlling A/ M door 6,7 is to have full-shut position (maximum cooling).The high-temperature high-pressure refrigerant of discharging from compressor 21 does not have radiations heat energy when by gas cooler 22.Therefore, in vaporizer 27, cooled air flows through conduit 2 to walk around gas cooler 22.For example, air is blown into passenger accommodation from face outlet, makes passenger accommodation be cooled to have the temperature (setting temperature) of expectation.Further, in inner heat exchanger, from outdoor heat converter 24, flowing through the high-temperature high-pressure refrigerant of h 25 and from reservoir 28, flowing through heat-shift between the low-temperature low-pressure refrigerant of low-temperature side heat exchanger 29.Therefore the high-temperature high-pressure refrigerant, flowing in vaporizer 27 is cooled.Therefore, vaporizer heat content increases, and makes to improve by saving power or electric power the cycle efficiency of refrigeration cycle 3.
When heating mode is selected as the operator scheme of refrigeration cycle 3, variable throttle valve 50 has pressure reducing mode, and solenoid valve 34 is opened.The refrigeration agent of discharging from the outlet of compressor 21 circulates in the following sequence: gas cooler 22, valve 50, outdoor heat converter 24, h 25, valve 34, reservoir 28, low-temperature side heat exchanger 29 and compressor 21 are (as shown in the black direction of arrow by Fig. 2, in the circulation loop for heating mode, Heating Cyclic).Now, valve 26 can be fully closed.
Now, the opening degree of controlling A/ M door 6,7 is to have full-gear (maximum heating).The high-temperature high-pressure refrigerant of discharging from compressor 21 when by gas cooler 22 by heat radiation to the air conduit 2.Air is blown into passenger accommodation from foot's outlet, makes passenger accommodation be heated to have the temperature (setting temperature) of expectation.In inner heat exchanger, do not carry out heat exchange, this is because low-temperature low-pressure refrigerant passes through each in heat exchanger 25,29.
When selecting dehumidification mode as the operator scheme of refrigeration cycle 3, variable throttle valve 50 has pressure reducing mode, and solenoid valve 34 is closed.The refrigeration agent of discharging from the outlet of compressor 21 circulates in the following sequence: gas cooler 22, valve 50, outdoor heat converter 24, h 25, valve 26, vaporizer 27, reservoir 28, low-temperature side heat exchanger 29 and compressor 21 are (as shown in the hacures direction of arrow by Fig. 2, at the circulation loop for dehumidification mode, dehumidifying circulation).
Now, air is cooled and is dehumidified in vaporizer 27, and air is reheated in gas cooler 22.Air is for example blown into passenger accommodation from DEF outlet or foot's outlet.Passenger accommodation dehumidified and heating so that passenger accommodation has the temperature (setting temperature) of expectation and removes or prevent that windshield from hazing.Can change by the throttling degree of variable throttle valve 50,26 head pressure of refrigeration agent and the refrigerant pressure of outdoor heat converter 24 of discharging from compressor 21.Therefore, control throttling degree, make heating efficiency (flowing out or flow into the temperature of the air passenger accommodation from gas cooler) or the dehumidifying effect (temperature of the air flowing out from vaporizer) of vaporizer 27 of gas cooler 22 there is desired value.
Particularly, if throttling degree is controlled to make the head pressure of refrigeration agent and the refrigerant pressure step-down (opening degree of valve 50: little of outdoor heat converter 24 from compressor 21 discharges, the opening degree of valve 26: large), outdoor heat converter 24 as (as) heat sink, making is increased by the heat of gas cooler 22 radiation.Therefore the temperature that blows that, is blown into the adjusting air in passenger accommodation has relatively high temperature.
By contrast, if throttling degree is controlled to make the head pressure of refrigeration agent and the refrigerant pressure of outdoor heat converter 24 of discharging from compressor 21 to uprise the (opening degree of valve 50: large, the opening degree of valve 26: little), outdoor heat converter 24 as (as) radiator, make to be reduced by the heat of gas cooler 22 radiation.Therefore the temperature that blows that, is blown into the adjusting air in passenger accommodation has relatively low temperature.
Next, the air conditioning control gear 10 with variable throttle valve 50 and control valve 50 by explanation heating.
As shown in Figure 1, variable throttle valve 50 comprises housing 51, valve base part 52, valve member 53, spring 54, motor 55, plate-shaped member 56, annular element 57, O ring 58 and reducing gear 59.
The lower end of the cylindrical shape part of shell 553 has at outward extending flange portion in the radial direction.O shape ring 58 corresponding to sealing component is inserted between flange portion and housing 51.Metal plate-like parts 56 are screwed into housing 51 by screw, and by being arranged in the annular element 57 of the flange portion top of shell 553, flange portion are pressed on housing 51.Therefore, can in whole periphery, between housing 51 and the shell 553 of motor 55, realize sealing.
The rotor 552 being arranged in shell 553 is made by magnetic material.Rotor 552 has approximate columnar body 552a and cylinder magnet 552b.A part of main body 552a is removed with annular recess shape from upper surface and lower surface.Cylinder magnet 552b is made by permanent magnet, and is arranged on the external peripheral surface of main body 552a.Cylinder magnet 552b is magnetized with proportional spacing in the sense of rotation of rotor 552.
Recess is limited in the main body 552a of rotor 552, and from the core of lower surface to fovea superior.The upper end of the axle 53a of valve member 53 is fixed in the top surface portion of recess.
Helical thread portion be formed on rotor 552 main body 552a the interior perimeter surface of recess on.On the other hand, cylindrical shape male thread portion 51b is fixed to housing 51, and to upper process.Outside thread is formed on the external peripheral surface of male thread portion 51b.
By combining reducing gear 59 that a plurality of gear configurations form, be arranged between the inner circumferential surface of recess and the external peripheral surface of male thread portion 51b of main body 552a of rotor 552.Reducing gear 59 can be for example by thering is sun gear and planetary planetary gears forms.Alternatively, reducing gear 59 can form by combining a plurality of spur wheel structures.
Reducing gear 59 have be formed on the helical thread portion engagement in the inner circumferential surface of recess of main body 552a of rotor 552 input gear and with the output gear that is formed on the outside thread engagement in the external peripheral surface of male thread portion 51b, and make the rotation of rotor 552 slow down and described rotation is passed to male thread portion 51b.
Therefore, the rotation of rotor 552 makes rotor 552 upper mobile at axial direction (on above-below direction in the accompanying drawings).Because adopt reducing gear 59 between rotor 552 and male thread portion 51b, so rotor 552 displacement amount is in the axial direction relatively little with respect to the rotating amount of rotor 552.
When rotor 552 rotates and moves on axial direction, be fixed to the also displacement of valve member 53 of the main body 552a of rotor 552, thereby change the opening degree between valve member 53 and valve seat 52a.
The structure being limited by motor 55, reducing gear 59 and the male thread portion 51b that is threaded with rotor 552 via reducing gear 59 can be corresponding to having stepping motor and controlling the electric driver of the opening degree of refrigerant passage by make valve member move according to the angle of swing of stepping motor.
As shown in Fig. 1 clearly, the axle 53a of valve member 53 has stepped part.Spring 54 is inserted between the top surface of main body 552a of stepped part and rotor 552.Therefore,, if rotor 552 is to bottom offset after valve member 53 is positioned on valve seat 52a, spring 54 is compressed, makes it possible to limit excessive load and is applied to the base portion being limited between valve member 53 and valve seat 52a.
In addition,, because be in contact with one another from the outstanding pin parts 51c of housing 51 with from the outstanding pin parts 552c of rotor 552, therefore can restrict rotor 552 there is excessive rotation displacement.
As shown in Figure 1, ECU10 has air conditioning controller with function 101, input processor 102 and driver element 103.Input processor 102 is processed from the signal of each switch or sensor input, and the signal after processing is sent to air conditioning controller with function 101.Driver element 103 exports to control each actuator (servomotor 13-15, blower motor 16, throttle valve 26, solenoid valve 34 or transducer 20) using the numerical information of being determined by controller 101 as electrical signal.
ECU10 also has stepper drive controller 111, driver element 113 and input processor 112.Stepper drive controller 111 receives the instruction of the opening degree about valve 50 of being determined by air conditioning controller with function 101, and according to described instruction, determines the activation bit (for example, current value) of motor 55.Particularly, for example, the number of steps (umber of pulse) of being set in the driving direction (sense of rotation) of motor 55 of valve 50 and the driving of the motor 55 of valve 50 by stepper drive controller 111.Drive unit 113 is controlled A phase coil 551A and the B phase coil 551B of excitation stator 551 by PWM according to the activation bit by the definite valve 50 of stepper drive controller 111.The current value of A phase coil 551A and B phase coil 551B is input to input processor 112, and input processor 112 is carried out feedback control with respect to stepper drive controller 111.
The instruction of the opening degree about valve 50 that 111 inputs of stepper drive controller are determined by air regulator controller 101, and determine the driving direction (sense of rotation) of motor 55 and the activation bit of number of steps (umber of pulse) such as valve 50 according to the instruction of input and actual valve opening degree.Further, stepper drive controller 111 can be determined the indication of current value by the change of definite operation cycle pattern, and described indication can be exported to driver element 113.
When selecting refrigerating mode as the operator scheme of refrigeration cycle 3, air regulator controller 101 is exported to stepper drive controller 111 by the indication of valve opening degree.The directive command variable throttle valve 50 of valve opening degree is opened completely.When selecting heating mode or dehumidification mode (dehumidifying heating mode) as the operator scheme of refrigeration cycle 3, air regulator controller 101 is exported to stepper drive controller 111 by the indication of valve opening degree.Directive command variable throttle valve 50 decompression and the swell refrigeration agent of valve opening degree, make the better air conditioning with carry out desired that becomes of the operating efficiency of refrigeration cycle 3.
Fig. 3 is the plotted curve of the relation between valve opening degree and refrigerant flow in each in diagram refrigerating mode, dehumidifying heating mode and heating mode.Variable throttle valve 50 has the instruction area of the valve opening degree being shown by solid line and stain.In heating mode, the suitable valve opening degree of instruction in the Small Flow Control region that refrigerant flow is relatively little therein.Under dehumidifying heating mode, the applicable valve opening degree of instruction in middle flow control area.Under refrigerating mode, in large flow region, instruction maximal valve opening degree is to have peak rate of flow.
Next, the opening degree that the valve 50 of being carried out by the driving-controlling device consisting of stepper drive controller 111, input processor 112 and driver element 113 of the present embodiment is described is controlled.Fig. 4 is the flow chart that illustrates the summary of the valve opening degree control of being undertaken by driving-controlling device.
As shown in Figure 4, driving-controlling device input is by the driving direction (opening direction) of the motor 55 of the definite valve 50 of air regulator controller 101 and number of steps (umber of pulse) and about the information (S210) of the change of operation cycle pattern.
Here, for the valve opening degree instruction of valve 50, be transfused to, and determine the driving direction (opening direction) of motor 55 and the activation bit of number of steps (umber of pulse) such as valve 50 according to the valve opening degree instruction of input and actual valve opening degree.Further, can for example according to the eigenvalue shown in Fig. 3, determine the change of operation cycle pattern.
Next, according to S210, determine whether operation cycle exists change (S220).When determining that operation cycle does not change in S220, determine whether the number of steps of being carried out by motor 55 (umber of pulse) is more than or equal to predetermined value (S230).
When determining that in S230 number of steps is not more than or equal to predetermined value (being less than predetermined value), current value A1 when normal (predetermined current value) is set to the current value (S240) of constant current driven.Then, by output current value, A1 carries out constant current driven, makes motor have rated speed R1 (S250).Then, driving-controlling device turns back to S210.
When determining that operation cycle does not change in S220, and when determining that number of steps is more than or equal to predetermined value in S230, (, although operation cycle does not change, larger in the change degree of determining valve opening degree, be more than or equal in the situation of predetermined value), driving-controlling device proceeds to S260.
In S260, determine after the last increase of current value, whether to pass by scheduled time T.The time passing from the last increase of current value is the time and then passing after carrying out described subsequently S270, S280 and S290.When determining that in S260 driving-controlling device proceeds to S240 since current value is last while also not passing through scheduled time T after increasing.
When increasing the current value of constant current driven by execution S270, S280 and S290, the temperature of driving-controlling device (assembly of driving-controlling device particularly) increases.Scheduled time T as the decision content in S260 is the threshold value for determining whether the temperature of the assembly of driving-controlling device after the increase temperature of following current value increases reduces.
Therefore,, when determining since current value is last while also not pass by scheduled time T after increasing, determine the inabundant reduction of temperature of the assembly of driving-controlling device in S260.If current value increases again, the assembly of possibility driving-controlling device may have excessive temperature, and may produce functional error, therefore forbids that current value increases.
When determining in S260 since current value is last while having passed scheduled time T after increasing, as the current value A2 (predetermined current value during High Rotation Speed) that is greater than current value A1, be set to the current value (S270) of constant current driven, this is because the temperature of the assembly of hypothesis driven control gear is fully reduced.Then, according to the command value of the umber of pulse of inputting in S210 with for the target revolution R2 (S280) of the predetermined permission Time Calculation motor 55 of varying cyclically.
After carrying out S280, with current value A2, carry out constant current driven to realize the target revolution R2 (S290) of motor 55.Then, driving-controlling device turns back to S210.
Therefore, when the heating mode in refrigeration cycle 3, when between the dehumidifying heating mode of refrigeration cycle 3 and three kinds of patterns of the refrigerating mode of refrigeration cycle 3, execution pattern changes, the present embodiment by stepper drive controller 111, the driving-controlling device that the driver element 113 of input processor 112 and ECU10 forms increases the current value for the constant current driven of motor 55, wherein in described heating mode, flow through the flow of refrigeration agent of refrigerant passage 51a of valve 50 less than or equal to the first predetermined value, in described dehumidifying heating mode, the flow that flows through the refrigeration agent of refrigerant passage 51a surpasses the first predetermined value and less than or equal to the second predetermined value, in described refrigerating mode, compare with the constant current value of using when implementing flow control in dehumidifying heating mode with the constant current value of using when implementing flow control in heating mode, flow through flow maximum in surpassing the flow region of the second predetermined value of the refrigeration agent of refrigerant passage 51a.
Therefore,, when the voltage of supplying from power supply changes, driving-controlling device can pass through stably drive motor 55 of constant current driven.
In addition, when valve opening degree therein in the small flow region less than or equal to the first predetermined value, change with the heating mode of decompression and swell refrigeration agent and valve opening degree wherein, surpassing in the intermediate flow region of the first predetermined value, change with decompression and the dehumidifying heating mode of swell refrigeration agent between during execution pattern change, the constant current value of using when changing in valve opening degree each pattern in pattern is compared, and the current value of the constant current driven of motor 55 increases.Therefore,, when changing pattern between heating mode and dehumidifying heating mode, the generation moment of torsion of motor 55 increases so that valve member 53 displacements can be changed rapidly valve opening degree.
In this case, the pattern that wherein valve opening degree changes when heating mode is corresponding to the first mode that wherein opening degree of refrigerant passage changes in the first flow region less than or equal to predetermined value, and the pattern that wherein valve opening degree changes when dehumidifying heating mode is surpassing corresponding to the opening degree of refrigerant passage the second pattern changing in the second flow region of described predetermined value.
In addition, when valve opening degree therein changes with the heating mode of decompression and swell refrigeration agent and dehumidifying heating mode and valve opening degree wherein in the small flow region less than or equal to the second predetermined value, surpassing and in the large flow region of the second predetermined value, changing so that between the refrigerating mode of valve opening degree maximum during execution pattern change, compare with the constant current value of using when heating mode changes in heating mode with dehumidifying when valve opening degree, the current value of the constant current driven of motor 55 increases.Therefore, when refrigeration agent be therein depressurized and the heating mode that expands and dehumidifying heating mode and refrigerating mode that wherein refrigeration agent is not depressurized under full opening mode between during execution pattern change, the generation moment of torsion of motor 55 increases so that valve member 53 moves, and makes promptly to change valve opening degree.
In this case, the pattern that wherein valve opening degree changes during heating mode in heating mode and dehumidifying is corresponding to the first mode that wherein opening degree of refrigerant passage changes in the first flow region less than or equal to predetermined value, and the second pattern that the pattern that wherein valve opening degree changes when refrigerating mode changes within surpassing the second flow region of described predetermined value corresponding to the opening degree of refrigerant passage.
As shown in Figure 5, if current value is set to constant, for example the A1 place during by constant current driven at the motor 55 when consisting of stepping motor, can not carry out High Rotation Speed, and this is to be reduced because generate moment of torsion in response to the instruction of the High Rotation Speed when the cyclic switching.In the present embodiment, when needing the cyclic switching of High Rotation Speed, current value is increased to A2 and generates moment of torsion to increase, and makes it possible to achieve High Rotation Speed.
Therefore, when valve opening degree therein in relatively little mobile control area reformed pattern and wherein valve opening degree when execution pattern changes between reformed pattern in relatively large mobile control area, can shorten the spent time of valve opening degree that reaches setting.In addition, do not need to increase the size of motor.
In addition, in the S260 shown in Fig. 4, when the last increase elapsed time from current value shortens (in short side) with respect to scheduled time T, when thereby the value of the physical quantity relevant with the temperature of the assembly of driving-controlling device is higher, even when pattern is switched, by carrying out S240 and S250, driving-controlling device also can be forbidden the increase of current value.
If the temperature of the assembly of driving-controlling device uprises, driving-controlling device may have functional error.Therefore, when the value of the relevant physical quantity of the temperature of the assembly with driving-controlling device is during higher than threshold value, even when pattern is switched, also can forbid the increase of current value, thus the increase of the temperature of the assembly of restriction driving-controlling device.Therefore, can limit driving-controlling device and there is functional error.In addition, in this case, although stepping motor becomes, be difficult to there is High Rotation Speed, owing to being applied to the electric power of motor 55, can reduce, therefore can improve operating efficiency.
In addition, in the S280 shown in Fig. 4, driving-controlling device is by the command value of the number of pulses of cyclic switching and the rotating speed of target of permission Time Calculation stepping motor, and in S290, driving-controlling device drives with realize target rotating speed by output steady current.Therefore, when cyclic switching (when pattern is switched), the rotating speed of stepping motor can be increased according to required degree, therefore can control the generation of the heat in driving-controlling device.
In addition, in the S230 shown in Fig. 4, even if be not when cyclic switching,, even in same pattern, when the change degree of valve opening is large,, when the umber of pulse while changing valve opening degree is more than or equal to predetermined value, driving-controlling device also allows stepping motor to have High Rotation Speed in S260, S270, S280 and S290.Therefore,, while switching even without pattern, also can shorten the spent time of valve opening degree that reaches setting.
In addition,, according to the present embodiment, heating is equipped with the reducing gear 59 of the rotation deceleration that makes stepping motor by variable throttle valve 50, and valve member 53 passes through reducing gear 59 by the swing offset of stepping motor.Although can make by being equipped with the reducing gear 59 that the rotation of stepping motor is slowed down, realize the high control accuracy that flows, if but stepping motor is only with ordinary rotational speed rotation, may need to expend chien shih valve member 53 when more and move when changing valve opening degree.Therefore, the disclosure is applied to be equipped with the valve 50 of reducing gear 59 very effective.
Although be omitted in the explanation of the cooling cycle system with reference to Fig. 2, but as shown in Figure 1, high pressure side refrigerant pressure sensor 40A is arranged the pressure in the refrigerant passage 51a of the upstream of valve member 53 for detection, that is, the refrigerant pressure before reducing pressure for detection of the refrigeration agent in 50 pairs of refrigeration cycle of valve.Stepper drive controller 111 can change according to the refrigerant pressure being detected by high pressure side refrigerant pressure sensor 40A the current value of the constant current driven of motor 55.Particularly, when the refrigerant pressure detecting becomes large, the current value of constant current driven can increase.
Therefore, the current value of constant current driven increases according to the increase of the refrigerant pressure of the upstream of the valve member 53 in refrigerant passage 51a.In this case, when load level increases, the current value of constant current driven increases the maximum moment of torsion that generates.
As shown in Figure 1, refrigerant pressure sensor 40A in high pressure side is arranged for detecting pressure in the refrigerant passage 51a of valve member 53 upstreams to detect in refrigeration cycle by the pressure of the refrigeration agent before throttle valve 50 decompressions.Yet sensor 40A is not limited in the refrigerant pipe of the direct upstream that is placed on throttle valve 50.For example, sensor 40A can be arranged in housing 51 to face the refrigerant passage 51a in the upstream of valve member 53.Further, head pressure sensor 40 can be used as high pressure side refrigerant pressure sensor and is shared.
Can increase according to the increase of the upstream side of the valve member 53 in refrigerant passage 51a and the pressure difference between downstream side the current value of constant current driven.Alternatively, can control constant current value according to the sensor information from three or more sensor transmissions.
Although omitted detailed description, cooling can have and the identical structure of variable throttle valve 50 for heating by variable throttle valve 26.Therefore, coolingly with variable throttle valve 26 and heating, by variable throttle valve 50, can be formed general.
The disclosure is not limited to above embodiment, but can in the situation that not deviating from protection domain of the present disclosure, by distortion, implement.
In above embodiment, when valve opening degree therein in the small flow region less than or equal to the first predetermined value, change with the heating mode of decompression and swell refrigeration agent and valve opening degree wherein, surpassing in the intermediate flow region of the first predetermined value, change with decompression and the dehumidifying heating mode of swell refrigeration agent between during execution pattern change, the current value that while changing within valve opening is surpassing the flow range of the first predetermined value (when valve opening changes in the flow range less than or equal to the first predetermined value with) used when changing in valve opening degree each pattern in pattern is compared, the current value of the constant current driven of motor 55 increases, but the disclosure is not limited to this.
For example, when the current value under the heating mode that valve opening degree changes in the flow range less than or equal to the first predetermined value is therein different from the current value under the dehumidifying heating mode that valve opening degree therein changes within surpassing the flow range of the first predetermined value, needed is only that current value when being increased in pattern and switching is to be at least greater than the current value in the heating mode of carrying out flow control in small flow region.
; when valve opening degree therein in the small flow region less than or equal to the first predetermined value, change with the first mode of decompression and swell refrigeration agent and valve opening degree wherein, surpassing in the intermediate flow region of the first predetermined value, change with decompression and the second pattern of swell refrigeration agent between execution pattern while changing, be neededly only and for change the opening degree of refrigerant passage current value used at first mode, compare the current value of increase constant current driven.
In addition, in above embodiment, when compare the time passing from last current value increase shorter (short time) with scheduled time T, thereby the temperature of the assembly of driving-controlling device is when still high, even when pattern is switched, driving-controlling device also can forbid that current value increases.That is, the time that passes is corresponding to the relevant physical quantity of the temperature of the assembly with driving-controlling device, but the disclosure is not limited to this.
When the value of other relevant physical quantity of temperature except the time of passing and assembly driving-controlling device make driving-controlling device assembly temperature higher than limit in advance threshold value time, even when pattern is switched, also can forbid the increase of current value.In addition, temperature that can direct-detection assembly, even and when pattern is switched, when detected temperatures is during higher than threshold value, also can forbid the increase of current value.
In addition,, in above embodiment, although omitted the explanation about the drive system using step of stepping motor, stepping motor can have full stepper drive or micro-stepper drive.In addition, resolution as required, can combine full stepper drive and micro-stepper drive mutually.
The tooth that full stepper drive represents its rotor 552 (for example, the magnetic pole of cylinder magnet 552b) method for driving from relative position one moved further of the tooth with stator 551 (for example,, by the magnetized magnetic pole of each phase coil) to the relative position of the tooth of described tooth with being next to stator 551.Micro-stepping enter to drive the tooth that represents rotor 552 wherein from the relative position of the tooth with stator 551, by a plurality of steps, to move to gradually the method for driving of the position relative with the tooth of described tooth that is next to stator 551.That is,, in micro-stepper drive, the driving angle of the step in full stepper drive is divided into multistep (make, the tooth of rotor 552 can be stopped between two teeth of stator 551).
In addition, in above embodiment, although variable throttle valve 50 is equipped with the reducing gear 59 that the rotation of stepping motor is slowed down, and valve member 53 by reducing gear the swing offset by stepping motor, the disclosure is not limited to this.It is effective that the disclosure is applied to not be equipped with the expansion valve device of reducing gear.
Except supercritical steam compressing hot pump circulation, refrigeration cycle 3 can be that wherein high side pressure is equal to or less than the vapor compression heat pump circulation of critical pressure.
Corresponding to the variable throttle valve 50 of expansion valve device with drive and the driving-controlling device of controlling variable throttle valve 50 can be applied to fixed refrigeration cycle except the refrigeration cycle for automotive air conditioner.
Claims (5)
1. an expansion valve device, described expansion valve device is arranged in refrigeration cycle (3) with decompression and the refrigeration agent that expands and circulate in refrigeration cycle, and described expansion valve device comprises:
Housing (51), described housing limits the refrigerant passage (51a) that refrigeration agent is flow through;
Valve member (53), described valve member is arranged in housing to change the opening degree of refrigerant passage;
Motor driver (55), described motor driver has stepping motor with by making valve member be shifted to control opening degree according to the angle of swing of stepping motor; With
Driving-controlling device (10), described driving-controlling device is with constant current driven and control step motor, wherein
Driving-controlling device changes with steady current execution pattern between first mode and the second pattern, in described first mode, the opening degree of refrigerant passage changes in the first flow region less than or equal to predetermined value at the flow of refrigeration agent that flows through refrigerant passage, in described the second pattern, the opening degree of refrigerant passage changes in the second flow region higher than described predetermined value at the flow of refrigeration agent that flows through refrigerant passage, and the value (A2) of steady current when driving-controlling device increase pattern changes is to be greater than the value (A1) of the steady current when the opening degree of refrigerant passage changes in first mode.
2. expansion valve device according to claim 1, wherein
Described driving-controlling device has the reducing gear (59) of the rotation deceleration that makes stepping motor, and
Described valve member is the rotation displacement by stepping motor by reducing gear.
3. expansion valve device according to claim 1 and 2, wherein
When the temperature of driving-controlling device is during higher than predetermined value, or when the value of the physical quantity with temperature correlation is during higher than predetermined threshold, even when pattern changes, driving-controlling device also can be forbidden the increase of the value of steady current.
4. according to the expansion valve device described in any one in claim 1-3, wherein
Described first mode is the puffing pattern that wherein refrigeration agent is depressurized and expands in the first flow region in the time must making to flow through the refrigeration agent decompression of refrigerant passage, and
Described the second pattern be wherein when the refrigeration agent that does not need flow by refrigerant passage reduces pressure valve member make the opening degree of refrigerant passage maximum so that flow through the full opening mode that the flow of the refrigeration agent of refrigerant passage becomes maximum in the second flow region.
5. according to the expansion valve device described in any one in claim 1-3, wherein
Described first mode is the first puffing pattern that wherein refrigeration agent is depressurized and expands in the first flow region,
Described the second pattern is the second puffing pattern that wherein refrigeration agent is depressurized and expands in the second flow region, and
The value of steady current when described driving-controlling device increase pattern changes is to be greater than the value of the steady current when opening degree changes in first mode and the value of the steady current when opening degree changes in the second pattern.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011-208295 | 2011-09-24 | ||
| JP2011208295A JP5445548B2 (en) | 2011-09-24 | 2011-09-24 | Expansion valve device |
| PCT/JP2012/005075 WO2013042303A1 (en) | 2011-09-24 | 2012-08-09 | Expansion valve device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103732964A true CN103732964A (en) | 2014-04-16 |
| CN103732964B CN103732964B (en) | 2015-11-25 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280040408.0A Active CN103732964B (en) | 2011-09-24 | 2012-08-09 | Expansion valve device |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US9816639B2 (en) |
| JP (1) | JP5445548B2 (en) |
| CN (1) | CN103732964B (en) |
| DE (1) | DE112012003944T5 (en) |
| WO (1) | WO2013042303A1 (en) |
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Also Published As
| Publication number | Publication date |
|---|---|
| DE112012003944T5 (en) | 2014-07-10 |
| CN103732964B (en) | 2015-11-25 |
| JP2013068294A (en) | 2013-04-18 |
| US9816639B2 (en) | 2017-11-14 |
| JP5445548B2 (en) | 2014-03-19 |
| WO2013042303A1 (en) | 2013-03-28 |
| US20140245778A1 (en) | 2014-09-04 |
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